Valve lifter means



y 14, 1968 Y J. E. STEINER 3,382,854

VALVE LIFTER MEANS Filed Jan. 24, 1966 3 Sheets-Sheet 1 INVENTOR.

JAMES E. STEINER ATTORNEY y 4, 1968 J. E. STEINER 3,382,854

VALVE LIFTER MEANS Filed Jan. 24, 1966 5 Sheets-Sheet 2 INVENTOR.

JAMES E. STEINER thud/AM ATTORNEY y 4, 1968 J. E. STEINER 3,382,854

VALVE LIFTER MEANS Filed Jan. 24, 1966 3 Sheets-Sheet :5

kF/G. /0

INVENTOR.

JAMES E. 'STEINER ATTORNEY United States Patent 3,382,854 VALVE LIFTERMEANS James E. Steiner, 427 N. Quentin, Wichita, Kans. 67208 Filed .Tan.24, 1966, Ser. No. 522,508 9 Claims. (Cl. 123-90) ABSTRACT OF THEDISCLUSURE This invention relates to valve lifters, and moreparticularly, to a speed responsive valve lifter. Still morespecifically, this invention is drawn to a valve lifter connectedbetween a rotating cam shaft and a pusher rod that is responsive toengine oil pressure to increase the normal axial movement of the pushernod and the resultant lift of the valve member connected thereto. Thisinvention particularly relates to valve lifters used in internalcombustion engines whereby the lift of the valve members is variable anda function of the engine speed and oil pressure to provide foreconomical and efiicient operation of the engine. Also, this inventionrelates to a valve lifter structure including a cylindrical housinghaving an enlarged bore, a piston means slidably mounted within the borefor movement perpendicular to the axis of the housing, a pusher seatmeans mounted within the bore engageable with a pusher rod for theactuation of a valve memher, and linkage means interconnecting thepusher rod seat means and the piston means whereby the pusher rod isextended varying amounts in response to engine speed by fluid pressuresupplied to the piston means.

Various types of valve lifters are known to the prior art which providefor self-adjusting operation to maintain Zero lash in the valveoperating linkage. The prior art devices use a special mechanicallinkage or hydraulic system to achieve the self-adjusting function;however, none of these devices teach the use of a speed responsive valvelifter to automatically vary the lift of the pusher rod and connectedvalve member for more efficient engine operation.

The invention, herein, provides a fi-ui-d controlled valve liftermounted substantially the same as a conventional valve lifter in aninternal combustion engine. This new and novel valve lifter isresponsive to oil pressure resulting from the engine speed to controland vary the amount of opening or lift of the valve members mounted inthe engine cylinders. This movement of the valve lifter results in avariable movement of a connected pusher rod and valve member whereby thevalve member is open more during high speed operation for greatereconomy and efiicient engine performance.

In a preferred embodiment of my invention, a valve litter is providedfor installation in an internal combustion engine between the lower endof a pusher rod and a rotating cam shaft. The valve lifter includes avalve casing slidably mounted within a stationary lifter housing whichis a part of the engine block. The casing has a central bore open at oneend and a pair of opposed cylindrical openings adjacent the lower end ofthe bore. A pair of piston means are slidably mounted within the boreand have laterally extended piston member-s mounted within thecylindrical openings. A valve seat means is slidably mounted within thebore for axial movement and interconnected to the piston means by a pairof linkage or lever arms. The upper end of the seat rneans has asemicircular groove adapted for contact with the lower end of the pusherrod. A ball bearing is rotatably mounted within the lower end of thecasing and adapted for engagement with the cam shaft for axial movementof the valve lifter.

ice

The conventional oil pump of the internal combustion engine supplies anoil fluid pressure which is variable according to engine speed. Thisvariable oil pressure is conducted by supply line through the valvecasing so as to be av'aliable to the cylinder openings and pistonmembers.

On operating above a certain predetermined fluid pressure, the pistonmembers are moved inwardly of the cylinder openings resulting in anupper axial movement of the valve seat means by said lever armsovercoming the force of the springs holding the valve members in theclosed posit-ions. This movement is in addition to the normal axialmovement caused by the rotating cam shaft thereby resulting in anadditional movement of the pusher rod and a further opening of the valvemember for greater operating efficiency at high engine speeds.

Accordingly, it is an object of this invention to provide a new andnovel valve lifter.

Another object of this invention is to provide a speed and oil pressureresponsive valve lifter for achieving variable lift.

Still another object of this invention is to provide a valve lifterhaving a hydraulic adjusting structure to maintain zero lash in thevalve structure for a quiet operation.

One other object of this invention is to provide a 'valve lifter havinga seat means contacting a pusher rod, which is held in the closedposition by a compression spring, piston means movable under fluidpressure, and a linkage means connecting said piston means and said seatmeans whereby the seat means is axially movable in one direction whenthe spring force on a pusher rod exceeds the fluid pressure and ismovable in the opposite direction when the fluid pressure exceeds thespring force on the pusher rod.

It is another object of this invention to provide a valve lifterresponsive to vehicle speed to progressively increase the lift of thevalve members at high speeds to a predetermined maximum value therebyincreasing the efficiency and horsepower output of the engine whilemaintaining a normal valve opening at idle and low speeds for maximumefiiciency.

Still one other object of this invention is to provide a valve lifterhaving the pusher rod connected to a hydraulically cushioned seat meansthereby providing for quiet and shock absorbing operation.

Another object of this invention is to provide a speed responsivevariable lift valve lifter of a simple rigid construction, that iseconomical to manufacture and having a simple method of operationthereby assuring substantially fail safe operation.

One other object of the invention is to provide a valve lifter havingthe lift of the valve member cont-rolled proportionally to the enginespeed whereby the compression ratio and fuel mixtures can be heldsubstantially constant throughout the variable speed ranges for betterengine operation.

A still further object of this invention is to provide a valve lifterhaving the valve lift and duration time thereof proportionate to theengine speed whereby the engine compression is stabilized resulting in aminimum amount of gasoline required with a resultant eflicient burningof the air-gas mixture for highly eflicient operation.

Various other objects, advantages and features of the invention willbecome apparent to those skilled in the art from the followingdiscussion, taken in conjunction with the accompanying drawings inwhich:

PEG. 1 is a perspective view of a conventional automotive internalcombustion engine having portions thereof broken away for clarity andillustrating a valve litter of this invention in combination therewith;

FIG. 2 is an enlarged perspective view of a valve lifter assembly ofthis invention;

FIG. 3 is an enlarged sectional view of the valve lifter of thisinvention;

FIG. 4 is a sectional view taken along line 4-4 of FIG. 2;

FIG. 5 is a sectional view taken along line 55 of FIG. 2;

FIG. 6 is a sectional view of the valve lifter of this inventionslidably mounted within a valve lifter housing and having the upper endof the valve lifter connected to a pusher rod and the lower end of thevalve lifter in operable engagement with a rotatable cam shaft andillustrating the relative positions of the pusher rod, valve lifter, andcam shaft When the valve member is in a closed position;

FIG. 7 is a sectional view of the valve lifter of this invention similarto FIG. 6 illustrating the relative arrangement of parts when in a valveopen position during low speed operation;

FIG. 8 is a sectional view of a valve lifter of this invention similarto FIG. 6 illustrating the relative arrangements of valve lifter partsafter the valve member has been actuated from the opened to the closedposition;

FIG. 9 is a sectional view of the valve lifter of this invention similarto FIG. 7 illustrating the valve in the opened position during highspeed operation;

FIG. 10 is an enlarged exploded perspective view of the valve lifter ofthis invention; and

FIG. 11 is an enlarged exploded perspective view of another embodimentof the valve lifter of this invention.

The following is a discussion and description of pre ferred specificembodiments of the new valve lifter means of the invention, such beingmade with reference to the drawings whereupon the same referencenumerals are used to indicate the same or similar parts and/orstructure. It is to be understood that such discussion and descriptionis not to unduly limit the scope of the invention.

Referring to the drawings and particularly to FIG. 1, a multi-cylinderinternal combustion engine, indicated generally at 18, includes a maindrive shaft powered by a plurality of piston and rod assemblies (notshown). The drive shaft 20 is connected by a chain 22 to a timing gear23 secured to one end of an elongated cam shaft 25. The cam shaft 25 hasa plurality of off-set cam portions 27 each of which is operablyassociated with a valve actuator assembly 28 adapted to sequentionallyactuate either an intake or exh'ause valve member 30.

As shown in FIG. 2, the valve actuator assembly 28 includes a curvedrocker arm 32 pivotally connected to a rigid shaft 33 secured to theengine block 35 and positioned adjacent the valve member 30. One end ofthe rocker arm 32 contacts the upper end of the valve member 30, and therocker arm 32 is rotatable, clockwise as viewed in FIG. 2, to move thevalve member 3% to an open position. It is seen that a compressionspring 36 mounted about the stem 37 of the valve member 30 biases thesame to a normally closed position. The other end of the rocker arm 32contacts the upper end of an elongated pusher rod 38 having the lowerend thereof in contact with a valve lifter 40 which is slidably mountedwithin a bore 41 in the engine block 3 5. A lower end portion of thevalve lifter 40 rides in contact with the cam shaft 25 whereby the valvelifter 40 is axially movable by the off-set cam portion 27.

The valve lifter 41 which actually presents the novelty in thiscombination and will be described in detail, is supplied with oilthrough galleries 43 and an oil inlet 44 to the bore 41 in the engineblock 35. An oil pump 46 is rotata-bly driven through a gear 47 andshaft 48 operably connected to the cam shaft 25 to supply oil through anoil filter 49 to the drive shaft 20, the galleries 43 for the valvelifters 40', etc. (FIG. 1). It is seen that the oil is supplied under apressure that varies directly as the speed of the pump 46 which variesaccording to the speed of the engine 18 to provide an importantoperating feature of this invention as will become obvious.

As shown in FIG. 3, the valve lifter 40 of this invention includes acylindrical valve housing or casing 51 having an enlarged bore 53 openat one end extended substantially two-thirds the length of the valvecasing 51. A pair of diametrically opposed cylinder openings 54 and 55extend transversely of the sidewall 56 of the casing 51 and arepositioned adjacent an end wall 58 of the bore 53. The other end of thevalve casing '51 has a hemispherical or domed-shape opening 60 openedoutwardly thereof. An axially extended passageway 61 positionedcentrally of the end wall 58 interconnects the bore 53 and the openings60. The outer peripheral edge of the other end of the valve casing 51 ischarnfered for ease of assembly. As shown in FIGS. 3 and 10, a ballbearing 63 is rotatably mounted within the dome-shape opening 60 andsecured therein by a snap ring 65 connected within a groove 67 in thesidewall of the opening 6i). It is seen that the snap ring 65 restrictslongitudinal movement of the ball bearing 63 while a lower portion ofthe bearing extends downwardly of the valve casing 51 for reasons tobecome obvious.

A pair of substantial identical piston means 69 and 71 are slidablymounted within the bore 53 for movement substantially perpendicular tothe axes of the valve casing 51. The piston means 69 and 71 are of asubstantially cordal cylindrical half-moon shape having outer curvedsurfaces 72 and 73 with laterally extended plunger or piston members 75and 76, respectively, integral therewith. The piston members 75 and 76are axially movable within the cylinder openings 54 and 55,respectively, in sealed contact with bushing members 78 which preventoil pressure leakage into the bore 53. The lower surfaces of the pistonmeans 69 and 71 engage the end wall 53 thereby assuring aligned axialmovement of the piston members 75 and 76 within the cylindrical openings54 and 55, respectively (FIG. 2). Additionally, it is noted in FIG. 5that the curved surfaces 72 and 73 of the piston means 69 and 71,respectively, and the inner surface of the bore 53 are of acorresponding contour and the piston end walls 80 and 81 are in aspaced, parallel relationship when the piston means 69 and 71 are in theextended position.

As shown in FIGS. 3 and 10, a cylindrical pusher rod seat means 83 ismounted in working engagement within the bore 53 for axial movementrelative thereto. The upper end of the seat means 83 has asemi-spherical groove 84 adapted to receive the lower end of the pusherrod 38 therewithin. An oil passageway 86 extends axially and centrallyof the seat means 83.

It is seen, therefore, that the piston means 69 and 71 are movabletransversely of the bore 53, whereas the seat means 83 is movableaxially thereof. A linkage or lever means 87 interconnects the pistonmeans 69 and 71 and the seat means 83 for conjoint movement.

The linkage means 87 consist of a pair of parallel lever arms 89 and alink arm 90 pivotally connected at one end to the piston means 69 and71, respectively, and at the opposite ends thereof to the seat means 83.As shown in FIG. 10, the lower ends of the lever arms 89 are extendedwithin parallel spaced slots 91 in the piston means 69 and pivotallyconnected thereto on a pin member 93 extended within a hole 94 in thepiston means 69 and a hole 96 in the lever arms 39. The link arm 90 issimilarly mounted within a slot 98 in the piston means 71 and pivotallymounted on a pin member 99 extended through a hole 101 in the pistonmeans 71 and a hole 103 in the link arm 90.

The upper ends of the lever arms 89 and the link arm 90 extend within adownwardly open, V-shape slot in the seat means 83 with the link arm 90extended between the lever arms 89 in nesting relationship. A lock pin107 extends transversely of the seat means 83 through a hole 163 andaxially aligned holes 109 and 111 in the lever arms 89 and the link arm90, respectively. It is seen, therefore, that the seat means 83 ispositively interconnected to the piston means 69 and 71 wherebytransverse movement of the piston means inwardly and outwardly of thesidewall 56 of the valve casing 51 results in upper and lower,respectively, movement of the valve seat means 83.

In the use and operation of the valve lifter 40 of this invention, onlythe operation of one valve actuator assembly 28 need be described as itis obvious that the multiple valve actuator assemblies 28 in the engine18 would function similarly. As shown in FIG. 2, the valve lifter 40 isslidably mounted within the bore 41 in the engine block 35 having oneend in contact with the pusher rod 38 and the ball bearing 63 at theother end riding in contact with the cam portion 27 of the cam shaft 25.The inner surface of the engine bore 41 has a cylindrical groove 113open to the oil inlet 44 whereby oil is supplied to the valve lifter 40to surround the outside of the valve casing 51 in operable engagementwith the piston members 75 and 76. It is seen that the valve seat means83 is axially movable singularly or in combination by (1) the axialmovement of the entire valve lifter 46 on rotation of the cam shaft 25,and (2) on movement of the piston means 69 and 71 under oil pressure.This axial movement of the valve lifter 4% is always against the bias ofthe compression spring 36 mounted about the valve stem 37. Therefore,when the engine 18 is on the off or inactive position, the valve lifter4t) assumes the position of FIG. 7 notwithstanding the rotationalposition of the cam shaft as there is no oil pressure against the pistonmembers 75 and 76 to overcome the force of the compression spring 36.

On operation of the engine 18 in the low speed range as shown in FIGS.6-8, the cam shaft 25 is rotating in the clockwise direction. Onapproaching the off-set cam portion 27 as shown in FIG. 6, the valvemember 30 and interconnected pusher rod 38 is in the lowered or closedposition under the force of the compression spring 36; however, thefluid pressure of the oil through the outlet 44 is greater than theforce of the expanded compression spring 36. Therefore, the piston means69 and 71 are moved inwardly so as to elevate the seat means 83 and bothzero lash in the valve lifter and an oil fluid cushion in the contactingparts for quiet and ellicient operation.

The oil pressure developed by the oil pump 46 is substantiallyproportional to the engine speed whereby the low speed operation isconsidered in the range of zero to 48 miles per hour with the oilpressure increasing to a maximum or" thirty pounds.

On rotation of the cam shaft 25 to the valve open position of FIG. 7 inthe low speed operation, the force of the compression spring 36 againstthe pusher rod 38 is greater than the oil pressure on the piston members'75 and 7 6 whereby the piston means 69 and 71 are fully separated. Theseat means 83 secured to the linkage means 37, assumes a lowermostposition relative to the valve casing 51 whereby the valve member 39 isopened only to the height of the cam portion 27 achieving the mostefficient low speed operation. It is noted that the vertical movement ofthe seat means 83 relative to the valve casing 51 is accomplished by thegradual increase of the force of the compression spring 36 over the oilfluid pressure thereby presenting a shockless, oil cushioned, quietmovement.

On movement of the valve lifter 4t and interconnected valve member 30from the open to the closed position shown in FIG. 8, the force of theprogressively expanded compression spring 36, decrease below the forceto the oil pressure whereby the piston means 69 and 71 move inwardly tothe position identical to FIG. 6. The previously described relationshipof force differential persists in this transfer with the oil pressureagain providing a fluid cushion for smooth transfer and Zero lash withinthe valve lifter 40.

In the high speed operation of the engine 18 namely, above approximately55 miles per hour, the oil pressure developed increases into a minimumvalue of approximately 35 pounds. During the valve closed positions inhigh speed operation as shown in FIGS. 6 and 8, the valve lifter 40assumes the same relative position as in the low speed, valve closedoperations because the oil pressure exceeds the expanded force of thecompression spring 36 as previously described. The primary novelty ofthe valve lifter 40 lies in the valve open position of FIG. 9 during thehigh speed operation whereby the oil pressure (at least 35 pounds)exceeds the force of the compression spring 36 to move the piston means69 and 71 inwardly. This movement is transferred by the lever means 87and results in an additional vertical movement of the seat means 83, thepusher rod 38, and the valve member 30 is actuated to a maximum openposition. It is seen, that this lift movement adds to the normal openingof the valve member 30 by the cam portion 27 of the cam shaft 25 forbetter intake and exhaust during the high speed operation.

This additional lift of the valve member 30 achieves a new and novelengine operation resulting in a more complete combustion, betterexhaust, and requires less gasoline with more eflicient air-gas ratiomixtures. Additionally, the very high compression ratios required forhigh speed operation would not be necessary with the new and novel valvelifter 40 to achieve the present day horsepower requirements.

Intermediate the high and low speed operations, namely between 48 and 55miles per hour, the oil pressure would gradually increase over the forceof the compression spring 36 resulting in the valve member 36- beingopened proportionately between the minimum and maximum open positions.This results in a smooth transfer with gradual efficient increase in theengine operation. It is obvious that the oil pressure could becontrolled to a maximum value of perhaps 35 to 38 pounds by the use of aconventional valve check (ball and spring type valve) installed withinthe supply line of the oil outlet 44 to limit the maximum pressure onthe valve lifter 40.

A second preferred embodiment of the valve lifter of this invention,indicated generally at 49a is shown in FIG. I I. This embodiment issubstantially identical to the valve lifter 40 having the same valvecasing 5 1, seat means 83, ball bearing 63, bushing members 78, and snapring as previously described. The difference arises in the connection ofthe seat means 83 to piston means 6 9a and 71a by linkage or lever arms116 and 1 17. The piston means 69a and 71a are mounted within the bore53 with the piston members 75 and 76 extended within the cylinderopenings '54 and 5d, respectively, in the casing 5 1. The lower end ofthe lever arm 1 16 is mounted Within a curved slot 118 in the pistonmeans 69a. The lever arm 117 is similarly mounted within a curved slotin the piston means 71a. The lever arm 116 has a longitudinally extendedslot .122 in the upper end thereof adapted to receive the upper tongueportion of the lever arm M7 in nesting or tongue and grooverelationship. Adjacent upper ends of lever arms 116 and 117 are mountedwithin the V-sh-aped slot 10-5 in the seat means 8 3 as described in thefirst embodiment of this invention.

It is seen that the valve lifter 46a presents a compact, readilyassembled package not requiring the use of high precision connectingpins and the like. The use and operation of the valve lifter 40a wouldbe identical to that previously described for the valve lifter 4G and,therefore, need not be described. It is obvious that the compressionspring 36 would exert a force through the pusher rod 38 to maintain thepinless valve lifter 40a in the assembled position.

As will be apparent from the foregoing description of the preferredembodiments of the applicants valve lifter means, relatively simple andinexpensive valve lifters have been described which are readilymountable in the conventional internal combustion engines now on themarket. These valve lifters provide a new and novel structure and meansof operation which provides greatly increased efliciency of operation.Applicants construction provides a quiet and zero backlash lifterassembly providing a minimum of wear on the contacting parts thereforeproviding a substantially maintenance free valve lifter.

While the invention has been described in connection with preferredspecific embodiments thereof, it will be understood that this inventionis to illustrate and not to limit the scope of the invention which isdefined by the following claims.

I claim:

I1. In an internal combustion engine having a valve member normally heldin the closed position by a resilient member, a valve lifter assemblyhaving pusher means connected between said valve member and a valvelifter, said valve lifter movable within a bore in the engine block toactuate said pusher means and open said valve member, and a fluid supplymeans to supply speed responsive variable fluid pressure to said valvelitter, the improvement of the combination comprising:

(a) a litter casing means having an opening at one end, the other end ofsaid casing means ada ted to be contacted to result in movement of saidcasing means,

(b) piston means slidably mounted within said casing means,

(0) pusher seat means slidably mounted within said casing means formovement relative thereto, one end of said pusher seat means adapted tocontact one end of said pusher means for movement thereof,

'(d) linkage means interconnected to said piston means and said pusherseat means whereby movement of said piston means results in movement ofsaid pusher seat means, and

(e) said piston means operably connected to said fluid supply means toprovide a fluid pressure to actuate said piston means to move saidpusher seat means and said pusher means against the force of saidresilient member to move said interconnected valve member to a greaterlift position at higher engine speeds.

2. 'A valve lifter as described in claim 1, wherein:

(a) said piston means including a pair of semi-circular disc-shapedactuator members having laterally extended piston members,

(b) said casing means having a pair of cylinder openings, and

(c) said piston members slidably mounted Within said cylinder openingsfor axial movement relative thereto, said piston members operablyconnected to the fluid supply means whereby said piston means is movableon variation of the fluid pressure.

3. A valve lifter as described in claim 2, wherein:

(a) said linkage means having a pair of lever arms, first pin memberspivotally connecting one end of said lever arms to respective ones ofsaid actuator members, and a second pin member pivotally connecting theother end of said lever arms to said pusher seat means whereby movementof said piston members of said cylinder openings results in an upwardaxial movement of said pusher seat means and the contacting pusher meanstoward the fully open valve position.

4. A valve lifter as described in claim 3, wherein:

(a) said piston members extended outwardly of said cylinder openingsduring the valve open, low speed, operation as the force of saidresilient member exceeds that of the fluid pressure from the fluidsupply means whereby said valve member is actuated to the normally openposition.

5. A valve lifter as described in claim 1, wherein:

(a) the fluid supply means maintains fluid pressure against said pistonmeans to assure constant contact of said pusher seat means /with saidpusher means thereby presenting a fluid dampener between parts for quietoperation, and whan the fluid pressure against said piston means exceedsthe pressure of said resilient member and said pusher means against saidpusher seat means, said piston means moves inwardly of said opening tomove said pusher seat means axially relative said casing and said pistonmeans 'for more efficient, quiet engine operation.

6. A valve lifter as described in claim 1, wherein:

(a) said pusher seat means movable axially to either a normallyextended, a closed, or a fully extended position to control the lift ofsaid valve member, and

(b) said piston means movable inwardly of said opening to raise saidpusher seat means when the speed responsive fluid pressure against saidpiston means exceeds the force of said resilient member, and

(c) said piston means remains in a normal outwardly extended positionrelative said opening on upward movement of said casing means when thespeed responsive fluid pressure against said piston means is below theforce of said resilient member.

7. A valve lifter as described in claim 6, wherein:

(a) said pusher seat means held in an extended position by the fluidpressure during the valve closed during low and high speed operation forquiet engine operation.

'8. A valve lifter as described in claim 6, wherein:

(a) said pusher seat means held in the fully extended position underfluid pressure during the valve open, high speed operation for eflicientengine operation.

9. In a valve train having a member resiliently biasing a valve member,said valve member operably connected with a valve lifter, said valvelifter comprising (a) a casing means having an opening at one end, the

other end of said casing means adapted to be contacted to result inmovement of said casing means,

(b) piston means slidably mounted within said casing,

(c) pusher seat means slidably mounted within said casing for axialmovement relative thereto, one end of said pusher seat means adapted tocontact one end of pusher means for movement thereof,

(d) linkage means interconnected to said piston means and said pusherseat means whereby movement of said piston means results in axialmovement of said pusher seat means, and

(e) said piston means operably connectible to a variable fluid pressuresupply means whereby a predetermined fluid pressure can actuate saidpiston means to move said pusher seat means and contacting pusher meansaxially against the force of the resilient member to move aninterconnected valve member.

References Cited UNlTED STATES PATENTS 1,210,081 1/1917 Sufla 123901,948,415 2/1934 Cooper 12390 2,326,883 8/1943 Pierce et al. 123-902,484,109 10/1949 Meinecke 12390 3,277,874 10/ 1966 Wagner 12390 ALLAVRENOE SMITH, Primary Examiner.

UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No. 3 ,382,854 May 14 1968 James E. Steiner e above identified It is certifiedthat error appears in th d as patent and that said Letters Patent arehereby correcte shown below:

line 60, after "axial" insert inwardly Column 7 "whan" should read whenColumn 8, line 8,

Signed and sealed this 23rd day of September 1969.

(SEAL) Attest:

Edward M. Fletcher, Jr. WILLIAM E. SCHUYLER, JR.

Commissioner of Patents Attesting Qfficer

